CN106715925A - Hydrostatic drive - Google Patents

Hydrostatic drive Download PDF

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Publication number
CN106715925A
CN106715925A CN201580049475.2A CN201580049475A CN106715925A CN 106715925 A CN106715925 A CN 106715925A CN 201580049475 A CN201580049475 A CN 201580049475A CN 106715925 A CN106715925 A CN 106715925A
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CN
China
Prior art keywords
pressure
swept volume
valve
hydraulic press
joint
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201580049475.2A
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Chinese (zh)
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CN106715925B (en
Inventor
M.马斯特
P.L.赫南德斯拉德拉
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of CN106715925A publication Critical patent/CN106715925A/en
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Publication of CN106715925B publication Critical patent/CN106715925B/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N7/00—Starting apparatus having fluid-driven auxiliary engines or apparatus
    • F02N7/08—Starting apparatus having fluid-driven auxiliary engines or apparatus the engines being of rotary type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/08—Prime-movers comprising combustion engines and mechanical or fluid energy storing means
    • B60K6/12—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • F15B1/033—Installations or systems with accumulators having accumulator charging devices with electrical control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/08—Prime-movers comprising combustion engines and mechanical or fluid energy storing means
    • B60K6/12—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator
    • B60K2006/126—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator the hydraulic accumulator starts the engine
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/46—Engine start hydraulic or electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20523—Internal combustion engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40523—Flow control characterised by the type of flow control means or valve with flow dividers
    • F15B2211/4053—Flow control characterised by the type of flow control means or valve with flow dividers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—Electronic controllers using input signals representing a temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention relates to a hydrostatic drive, which is used in particular to start an internal combustion engine. The drive comprises a hydraulic machine, which can be adjusted in the swept volume thereof from a maximum positive swept volume to a maximum negative swept volume via a zero swept volume by means of a hydraulic adjusting device and which can be operated as a pump with positive swept volume and as a motor with negative swept volume, a high-pressure accumulator, from which the hydraulic machine can be supplied with pressure medium for operation as a motor via a pressure line, which extends between a pressure connection of the hydraulic machine and the high-pressure accumulator, an accumulator-closing valve having a first position and a second position, which is arranged in the pressure line and by means of which a fluidic connection from the high-pressure accumulator to the hydraulic machine is open in the first position and closed in the second position, and an electronic control unit, in accordance with the signals of which the accumulator-closing valve can be actuated. The problem addressed by the invention is that of designing the hydrostatic drive in such a way that the components of the hydraulic machine are not subjected to high wear and a quick return from the range of negative swept volumes occurs. This problem is solved in that, in the event of an adjustment of the hydraulic machine from a negative swept volume to a positive swept volume, the electronic control device gives a signal for switching over the accumulator-closing valve from the first position to the second position and in that the accumulator-closing valve does not switch over to the second position until there is a zero swept volume or a positive swept volume of the hydraulic machine.

Description

The drive device of hydrostatic
The present invention relates to a kind of drive device of hydrostatic, it is especially arranged for starting internal combustion engine, especially diesel oil Motor, and with the feature of the preamble from claim 1.
Known a kind of drive device of hydrostatic from the A1 of WO 2012/125798, it has hydraulic press, the hydraulic press Start internal combustion engine in the operation as hydraulic motor and hydropneumatic high pressure accumulator is loaded in the operation as pump And the consumable component of other hydraulic pressure can be supplied using pressure medium.
The hydraulic press by means of hydraulic pressure adjusting means in its swept volume from maximum positive swept volume through zero passage Swept volume can adjust the negative swept volume of maximum, wherein, it is for positive swept volume, it is understood that there may be pump operation and right In negative swept volume, it is understood that there may be motor operation.Here, the swept volume is pressure medium amount, the pressure medium amount for Each revolution of power transmission shaft from the hydraulic press feed or is swallowed.For the operation as hydraulic motor, from high pressure storage By pressure line in device（The pressure line is moved towards between the compression fittings and high pressure accumulator of the hydraulic press）Using pressure Power media is capable of supply that the hydraulic press.Memory stop valve with first position and the second place is arranged in the pressure line Lu Zhong, wherein, the memory stop valve towards hydraulic press from the high pressure accumulator fluidly connecting portion in first position Open and end in the second position.Depending on the signal of the controller of electronics can actuate the memory stop valve.
Generally there are adjusting means for the hydraulic pressure of the swept volume of the machine of hydrostatic one or more regulations to live Plug（Regulation chamber is abutted to the regulating piston）With at least one return spring, caused in default institute in the presence of the return spring The hydraulic press is adjusted onto predetermined swept volume during the pressure-loaded for stating regulation chamber.
The targeted task of the present invention is to set up a kind of drive device for starting the hydrostatic of internal combustion engine, Wherein, can rapidly and without component excess load adjusted from the adjustment region with negative swept volume Hydraulic press.
This task is solved by the drive device of the hydrostatic with the feature in claim 1.
In the drive device of hydrostatic of the invention, hold towards positive work from negative swept volume by hydraulic press During product regulation, the controller of the electronics from first position by the memory stop valve then just given for being switched to the Signal in two positions so that the memory stop valve in zero swept volume of the hydraulic press or positive swept volume It is switched in the second place.Therefore ensure that, in the time（From maximum negative swept volume to the tune of zero swept volume Section requires the time）Period, also exist from the compression fittings of the hydraulic press and fluidly connect portion towards high pressure accumulator.Thus It is ensured that, pressure line is not evacuated and thus occurs without hole by the hydraulic press, and the hole can result in the damage of component Wound.Respectively according to the type of adjustment equipment, now the pressure in pressure line can be also used for：Adjusted using pressure-loaded Chamber, the pressure-loaded in the regulation chamber is acted as in the meaning being adjusted towards the direction of zero swept volume from negative swept volume With, thus can not only using the adjustment equipment return spring power, and can using be used for by the hydraulic press from The extruding force resetted in region with negative swept volume.
Favourable structural scheme of the invention can be found out from dependent claims.
The hydraulic press of regulation is known to, the hydraulic press has adjusting means, the adjusting means includes being abutted to the first tune First regulation chamber of section piston（For the regulation chamber, can control to facilitate by valve gear and hold towards maximum negative work The influent stream of the pressure medium that long-pending direction is adjusted and drainage can be controlled）, be abutted to the second regulating piston second tune Section chamber（The regulation chamber is fluidly connected with the pressure line and the regulation chamber is in the direction of the negative swept volume towards maximum Regulation in reduce and increase in the regulation towards the direction of maximum positive swept volume）And return spring, the return bullet Spring works towards the direction of maximum positive swept volume.When chamber is adjusted by from pressure off-load, such hydraulic press is conditioned Onto maximum positive swept volume.The first regulating piston is abutted to by entering to flow to pressure medium（The effect of the regulating piston Acting surface of the face more than second regulating piston）In the regulation chamber at place, the hydraulic press can be held from maximum positive work Product is adjusted by zero swept volume is straight towards maximum negative swept volume.Herein, thus described second regulation chamber in all the time In the presence of the pressure present in the pressure line, so as to during the hydraulic press resets from motor operation, be maintained During pressure in the pressure line, when without other control unit, by valve so that a kind of extruding force contributes to this Reset.
For controlling the influent stream of pressure medium and the valve gear of drainage from the first regulation chamber to preferably include control valve, By the control valve, for the regulation of the negative swept volume towards the first regulation chamber, the working joint is not relied on, from pressure The hydraulic press can be supplied in medium source, especially from high pressure accumulator using pressure medium.
For the operation of the hydraulic press as pump, the valve gear includes the adjuster of hydraulic pressure, and the adjuster is additional to institute State control valve and exist.For the adjuster with hydraulic pressure and the mating reaction with high pressure accumulator, the tunnels of control Fa Shi 3/2 Valve, the control valve carries the first joint（The joint is fluidly connected with the regulation pressure output end of the adjuster of the hydraulic pressure）And And with the second joint（The joint is fluidly connected with the pressure medium source）And with the 3rd joint（The joint with it is described First regulation chamber is connected）, and wherein, the control valve has first position（In the first position, the output end and the One input is fluidly connected and the second input ends）And the second place, in the second place, the output end and the Two inputs are connected and first input end ends.Thus, the adjuster of the hydraulic pressure is in the first position of the control valve The swept volume of the hydraulic press can be influenceed, and without effect in the second place of the control valve.
Especially, the adjuster of the hydraulic pressure is load-sensing（LS）Regulating valve, the regulating valve is flowed into institute in pressure medium By the pressure-loaded in the pressure line and in pressure medium from institute in the meaning in the first regulation chamber for stating adjusting means State in the meaning flowed out in the first regulation chamber by regulation spring and be present in LS joints（X）The LS control pressures loading at place, and Wherein, also LS control pressures are given to the load-sensing in the negative swept volume of the hydraulic press（LS）The LS of regulating valve Joint.By correspondingly selecting the LS control pressures, at least LS control pressures signal（The LS control pressure signals are previously given The LS control pressures）, then can be accomplished that, on the one hand also rapidly adjust institute from the region with negative swept volume State hydraulic press, but simultaneously non-regulated until maximum positive swept volume.It hereby is obtained that, the internal combustion engine is by the hydraulic pressure Machine is not loaded optionally and rapidly can speed up and run in idler revolutions after starting.
Advantageously, it is loaded with the load-sensing using LS control pressures（LS）Regulating valve, and the control valve is also In its second place.As long as the control valve is also located in its second place, then the loading holding of the LS regulating valves does not have Have an impact, because its control output end is not connected with the described first regulation chamber.Preferably, the LS control pressures even convergence Memory pressure, as long as control valve occupies its second place.Then the instantaneous of the switching of valve is being controlled, in the presence of suitable LS Control pressure, and need not also fill control circuit or so that the moveable control volume of valve makes larger stroke.
Advantageously, the LS control pressures are for example less than the pressure in the pressure line to adjust the pressure equivalent of spring Power（When the hydraulic press reaches zero swept volume when back swinging from maximum negative swept volume）, so that the hydraulic press Be conditioned by zero swept volume, but simultaneously non-regulated until maximum positive swept volume.The LS control pressures with it is accurate Value（The value has been obtained from the pressure equivalent of the regulation spring and the difference of the pressure in the pressure line）Deviation Balanced in the case of the swept volume for only slightly deviateing from zero swept volume, particularly handed over after zero in swept volume, The hydraulic storage is separated with the hydraulic press, and the pressure in the pressure line with less hydraulic capacity Must also just change.
Preferably, when the control valve is also located in its second place, LS control pressures have been given to described and have born Carry sensing（LS）The LS joints of regulating valve, wherein, the LS control pressures with fixed pressure differential, are stored in the high pressure first Below pressure in device, the memory pressure of decline is followed, and wherein, at least described previously given LS control pressures LS control pressures signal keeps constant, when during the control valve is changed to its first position from its second place.Herein can Happens is that, the LS control pressures are not corresponded to by the previously given value of LS control pressure signals, because from memory pressure The LS control pressures signal is derived, and in the position of the fluid path between high pressure accumulator and hydraulic press（In the position Place is put, control oil is taken out, for generating the LS control pressures）The pressure at place, due in the high pressure accumulator and hydraulic pressure The pressure loss based on the flow of fluid between machine and be less than desired LS control pressures.Real-time LS control pressures are but Can not be higher than such pressure：The LS control pressures are generated from the pressure.Thus then the LS control pressures with Pressure in fluid path further reduces, although the LS control pressures signal keeps constant.If in the control valve What is switched is instantaneous, and the real-time LS control pressures are equal to or are less than with the pressure equivalent less than the regulation spring The pressure in the LS regulating valves is applied in the reverse direction, then this LS regulating valve is located in such position：Wherein, described One regulation chamber is connected with storage tank.The hydraulic press is then soon from the region of negative swept volume towards the side of zero swept volume To regulation.If due to the instantaneous special situation of the switching in the control valve, the real-time LS control pressures are with big The pressure being applied in the reverse direction in the LS regulating valves is less than in the pressure equivalent of the regulation spring, then this LS regulations Valve is also located in such position first：Wherein, the first regulation chamber is connected with pressure line.The hydraulic press and then slightly It is micro- to be maintained in motor operation more long.Pressure in the pressure line and in high pressure accumulator declines, so that the LS Regulating valve enters in such position：Wherein, first chamber towards storage tank off-load is adjusted.
Show, when the difference of the fixation between memory pressure and LS control pressure signals is the LS regulating valves When adjusting about 1.75 times so big of pressure equivalent of spring, the hydraulic press rapidly back swing and will not towards compared with Big positive swept volume is shown.
It is possible that the drive system of the hydrostatic only relies upon the rotating speed of hydraulic press and in high pressure accumulator Pressure is controlled, and using pressure recorder detects the pressure.
At this moment more accurate control and more quick reset show as feasible：That is, being furnished with when the hydraulic press is used for During the logger of swept volume, and when after control valve is switched in first position from the second place, the LS controls are pressed The size of power, the size for being sized depending on the memory pressure and negative swept volume of at least described LS control pressures signal or When the change of the negative swept volume of person is to determine.
If there is logger for swept volume, control valve is being switched in first position it from the second place Afterwards, namely after starting process terminates, the memory stop valve depends on being sized to for detected swept volume It is switched in the second place from first position.
The embodiment of the drive device of hydrostatic of the invention is shown in the drawings.According to the unique of accompanying drawing Figure explains the present invention in further detail now.
Fig. 1 shows the line map of the embodiment.
In Fig. 1 as the drive device of the hydrostatic shown in line map except for starting diesel motor, being also used for Operation and equipment and manoeuvre portion 1 and the consumable component 2 of other hydraulic pressure including hydrostatic for actuating mobile work machines. The drive device combination diesel motor 4 is used, and the rotating speed of the diesel motor passes through the revolution speed sensing not shown in further detail Device come detect and the drive device bent axle 6 coupled to hydraulic press 10 power transmission shaft 8, the hydraulic press passes through in its swept volume Zero passage swept volume can be adjusted between positive swept volume and negative swept volume, and the hydraulic press is configured in oblique disk structure form In axial piston machine.Here, the swash plate is stroke control element, the stroke control element passes through its position, it is determined that The swept volume of the hydraulic press between maximum positive swept volume and the negative swept volume of maximum.Such axial piston machine is also referred to as It is the axial piston machine that can be swung completely.Its shell 12 has storage tank joint T and compression fittings P, wherein, the two joints T and P Enduringly and clearly arrange to high pressure and storage tank pressure.It is described can oscillatory completely be accomplished that, be maintained pump fortune Positive swept volume in row（Wherein, pressure medium is drawn and is given by the hydraulic press by storage tank joint T from storage tank 13 To in compression fittings P）When rotation direction in the case of, and in motor operation（In the motor operation, pressure medium is from pressure Power media source is flowed towards the compression fittings P, and the pressure medium is flowed out in storage tank 13 by the storage tank joint T）In During negative swept volume, hydraulic press 10 is run.
The compression fittings P by branch pressure line 14 and the manoeuvre portion 1 and other consumable component 2 and and high pressure Memory 16 is connected.In addition, the pressure line 14 has branch 18.Below, it should discuss high pressure accumulator respectively, i.e., Multiple high pressure accumulators as shown are made to be connected in parallel to each other.
The branch 18 and on the other hand between the manoeuvre portion 1 and other consumable component 2 on the one hand, be provided with by It is configured to the consumable component stop valve 20 of 2/2 way reversing valve.It in the base position by spring through pretension, by the manoeuvre portion 1 It is connected with other consumable component 2 with the compression fittings and high pressure accumulator 16 of hydraulic press 10, and it is in the on-position through actuating The pressure line 14 is directly ended towards the manoeuvre portion 1 and consumable component 2.
Pressure at the compression fittings P is hereinafter referred to as pump pressure.The pressure（Even if being deposited in hydraulic press and high pressure Connecting portion between reservoir is opened wide）Memory pressure can be deviated from based on flow losses.
Between the branch 18 and the high pressure accumulator 16, memory stop valve is provided with pressure line 14 22, the memory stop valve is in the base position by spring through pretension along from high pressure accumulator 16 towards the He of branch 18 The flow direction of hydraulic press 10 is ended, and the memory stop valve is caused in the height in the on-position through actuating The portion of fluidly connecting between pressure memory 16 and hydraulic press 10 is opened wide.In the base position of the memory stop valve 22, from The hydraulic press 10 to the pressure medium flow of high pressure accumulator 16 is feasible.
The hydraulic press 10 of axial piston machine for being configured to swing completely possesses adjusting means, and the adjusting means is basic Upper to have the first regulating piston 26, the regulating piston reacts on the second regulating piston 28 and return spring 29.Described first adjusts Save the acting surface of the acting surface more than second regulating piston 28 of piston 26.The regulating piston 26 defines regulation chamber 30. By valve gear 31 with controlling, pressure medium can be provided to regulation chamber 30 and from the regulation chamber 30 by chamber joint 32 Discharge.Second regulating piston 28 defines regulation chamber 33, and the regulation chamber is enduringly flowed in the shell 12 with the compression fittings P Body is connected.In the inactive state of the hydraulic press, cut down faster by leakage in the regulation chamber 30 and described Pressure in pressure line 14, so that the hydraulic press is adjusted in the positive swept volume of maximum by return spring 29. When filling the regulation chamber 30, the hydraulic press 10 is from maximum positive swept volume towards less positive swept volume toward backswing It is dynamic.In the filling for persistently carrying out in the regulation chamber 30, the hydraulic press 10 swings through zero swept volume, and backward Negative swept volume until adjusting to maximum negative swept volume.
The valve gear 31 includes three 3/2 ratio road valves, namely load-sensing regulating valve（LS regulating valves）40th, pressure is adjusted Section valve 39（The pressure-regulating valve is also referred to as hereinafter provided with the pressure-feed of reference 45 together with the LS regulating valves 40 Throttle regulator, and the pressure-regulating valve be set to be located at more than the load pressure that generally occurs within and high pressure accumulator 16 most On pressure more than big boost pressure）And it is configured to the control valve 48 of switching valve.The pressure-regulating valve 39 possesses first Joint, the joint can be connected by unloading circuit with storage tank 13.Second joint of the pressure-regulating valve 39 rests on described At compression fittings P.The 3rd joint that can be connected with first joint or with the second joint is by the pressure-feed stream The joint 46 of the regulation chamber side of adjuster 45 can be connected with the regulation chamber 30 at the regulating piston 26.LS regulating valves 40 First joint is rested at the unloading circuit, and the second joint is rested at the compression fittings P.The 3rd of LS regulating valves 40 connects Head can be connected with its first or second joint and enduringly be connected with the first joint of the pressure-regulating valve 39.The pressure The pushing block not shown in further detail of force regulating valve 39 is adjusting the 3rd joint in chamber 30 and the LS regulating valves by compression spring Connection meaning in load, and loaded in the meaning that the regulation chamber is connected with the compression fittings P by pump pressure. The pushing block not shown in further detail of LS regulating valves 40 in the 3rd joint and first joint and thus with the unloading Loaded by regulation spring 41 in the meaning of the connection of circuit and by being present in the LS pressure of the LS joints X and the 3rd Loaded in joint and second joint and the meaning being thus connected with the compression fittings P.In the valve 40 Domination has dynamic balance at pushing block, and the power for adjusting spring 41 is corresponded to when existing between the pump pressure and the LS pressure It is poor when.Generally, the difference is located between 10 bar and 25 bar.This difference also referred to as pressure equivalent of regulation spring or referred to as pump Δp.Currently, the pump Δ p may be calculated as 22 bar.
The LS pressure is the maximum load pressure or previously given LS in consumable component 1 and 2 simultaneously through actuating Control pressure.The maximum load pressure of the consumable component 1 and 2 is by carrying reversal valve of the reversal valve 54 as last chain link Chain is taken, and is reported in the common LS reporting lines 36 of this consumable component.In the maximum load of the consumable component 1 and 2 of hydraulic pressure Maximum pressure between pressure and previously given LS control pressures is selected by reversal valve 38 to reach, in the reversal valve First input end at there is the maximum load pressure of consumable component 1 and 2, the second input of the reversal valve by LS valves 44 with The pressure line 14 can be connected and the output end of the reversal valve connects with the LS at the pressure-feed throttle regulator 45 Head X is connected.Nozzle is disposed between second input and the LS valves 44 of first reversal valve 38.Also this can be saved Nozzle.
In the base position by spring institute pretension of LS valves 44, the second input of the reversal valve 38 is relative to pressure End and be connected with storage tank in line of force road 14.It is powered by the electromagnet for attracting, the LS valves 44 are trapped in on-position, In the on-position, the pressure of the pump circuit 14 is given the second input end of reversal valve 38 and when this pressure ratio Pressure at the first input end of the reversal valve 38 gives the output of this reversal valve when higher.
Nozzle 64 is linked into from the output end of the reversal valve 38 and is connect towards the LS of the pressure-feed throttle regulator 45 In the LS reporting lines 56 of head X guidings.Between this nozzle and the LS joints X of the pressure-feed throttle regulator 45, can The pressure limit valve 62 of regulation ratio is connected to the LS reporting lines 56, and the output end of the pressure limit valve is connected with storage tank. The pressure of the pressure limit valve is set by ratio electromagnet constantly in minimum value and such as maximum of 300 bar between Can change.The pressure limit valve 62 is such pressure limit valve：It carries negative characteristic, pressure set points because And reduce with the increase of the energization of the electromagnet.By means of the nozzle 64 and the pressure limit valve 62, from presence In pump pressure in pressure line 14, LS control pressures can be produced in the LS reporting lines, the LS control pressures Less than the pump pressure.
The control valve is linked into the shell 12 of the pressure-feed throttle regulator 45 and the hydraulic press 10 in configuration aspects Between.It possesses the first joint 66, and the joint is connected by circuit 67 with the section of the pump circuit 14, and the section is deposited described Reservoir stop valve 22 is connected with the high pressure accumulator 16.Second joint of the control valve 48 is adjusted with the pressure-feed stream The joint 46 of the regulation chamber side of section device 45 is connected.3rd joint of No. 3/2 valve and the phase of chamber joint 32 in the regulation chamber 30 Even.
In the base position by spring institute pretension of control valve 48, the joint 66 of the control valve 48 is ended.Institute The joint 46 for stating pressure-feed throttle regulator 45 is connected by control valve 48 with the chamber joint 32, so that the pressure-feed Throttle regulator 45 can adjust the hydraulic press 10.Control valve 48 is switched to it and connect by what the electromagnet by attracting was facilitated In logical position, the second joint of the pressure-feed throttle regulator 45 and thus joint 46 is cut off, and high pressure storage Device 16 is connected with the chamber joint 32.
The valve 20,22,38,44,54,62 and 64 is combined to start stopping valve block 52.Additionally, pressure sensor 75 （The memory pressure that branch is fitted in high pressure accumulator 16 is detected using the pressure sensor）With temperature sensor 76（Using this Temperature sensor detects the temperature of the pressure medium）Seat is placed at this valve block 52.
The control list that the startup function of the drive device of the stopping function and hydrostatic of the diesel motor 4 passes through electronics Unit 80 controls, and the control unit is connected by the circuit 81 of electricity with the pressure sensor 75, using electric circuit 82 and band The electromagnet for having pressure limit valve 62 is connected, is connected with the electric component at the diesel motor 4 using multiple circuits 83, with And be connected with the valve 20,22,44 and 48 for being capable of electromagnetic actuation and with various other sensors using other electric circuit.
For the diesel motor for operating, the valve 20,22,44 and 66 occupies position shown in the accompanying drawings.The consumable component Thus stop valve 20 allows to supply the consumable component 1 and 2 of the hydraulic pressure using pressure medium.The LS valves off-load leads to the storage Second input of the reversal valve 38 of case, so as in the output of the reversal valve and thus in pressure-feed throttle regulator The maximum load pressure of the consumable component 1 and 2 of the hydraulic pressure through actuating is there is at 45 LS joints X.The pressure limit valve 62 electromagnet is so powered：So that the pressure limit valve is set on about 210 bar.The pressure limit valve 62 by The LS control pressures are limited to about 210 by this for the operation of the load-sensing-be conditioned of the consumable component 1 and 2 of the hydraulic pressure Bar is upper and pump pressure of pump Δ p 22 bar high is limited on about 230 bar.Thus, using the pressure limit Valve 62, the operation for the load-sensing-be conditioned of the consumable component 1 and 2 of the hydraulic pressure realizes so-called pressure cut off.The control With the regulation chamber 30 be connected the joint 46 of the regulation chamber side of the pressure-feed throttle regulator 45 by valve processed.Thus, it is overall On, cause to be adjusted according to load-sensing in known manner, using the restriction of the pump pressure carried out by pressure limit valve 62, profit It is feasible that the consumable component 1 and 2 of the hydraulic pressure is supplied with pressure medium.Here, the high pressure accumulator is by the memory Stop valve 22 and its return valve function are supercharged to highest, the pump pressure occurred during the consumable component of the hydraulic pressure is actuated On.
But, this maximum pump pressure for occurring is due to by so-called second pressure limiting that valve carries out for consumable component Pressure limit and be less than the memory pressure needed for for starting the diesel motor.If situation thus is determined：The situation Show the disconnection of the diesel motor（Stop）, then there is such situation：Wherein, although do not actuate the hydraulic pressure One of consumable component 1 and 2, but the diesel motor then should first close the consumption for other reasons without being turned off Part stop valve 20 and then the high pressure accumulator is pressurized on desired boost pressure.In addition, the LS valves 44 enter Enter in on-position, in the on-position, the second input of the reversal valve 38 is connected with the pressure line 14.It is described Pressure limit valve 62 is set to such pressure value by the corresponding energization of the electromagnet that the controller 80 of electronics passes through subordinate On：The pressure value is located at the pump Δ p and passes through detected by the pressure sensor 75 and report to the controller Below 80 memory pressure.Due to nozzle 64, then be set at the pressure at the pressure limit valve be present in the pressure- At the LS joints X of feed throttle regulator 45.From the pressure value of starting, now by flowing by the electric current of the electromagnet The reduction of ramped shaped, little by little improves the setting pressure at the pressure limit valve 62.Existed by the setting pressure The degree of temporal change, the volume flow of the hydraulic press 10 as pump work can be set by the LS regulating valves Amount, the high pressure accumulator 16 is loaded using the volume flow.If desired memory pressure is, for example, 292 bar, Then the pressure set points of the pressure limit valve 62 do not continue to improve, when 270 bar has been reached in this place.The LS valves 44 It is again introduced into its resting position, the pressure limit valve 62 temporarily maximum can be powered, so as to by by internal leakage Or the nozzle do not drawn in Fig. 1 or the flow control valve towards the storage tank abatement that carries out accelerates in the LS report lines Pressure abatement in road 56.
If the diesel motor is now not switched off, the hydraulic press 10 so sets in pump operation：So that The standby pressure of 22 bar is just also maintained in the pressure line 14, the standby pressure is equal to pump Δ p.If have turned off Diesel motor, the then naturally described disengaging of hydraulic press 10 runs and passes through the return spring 29 and adjusts to maximum positive work appearance In product.The high pressure accumulator 16 is supercharged on the memory pressure of maximum, such as 292 bar.
If the diesel motor is again started up, the consumable component stop valve 20 and the control valve 48 are only actuated first. The latter enters in such position：Wherein, the regulation chamber 30 is by control valve 48 and the circuit 67 and the liquid Pressure memory 16 is connected.The regulation chamber 30 is thus loaded using memory pressure, thus the hydraulic press from it is maximum just Swept volume is adjusted by zero swept volume towards maximum negative swept volume.Here, by the regulating piston 26 Power produced by memory pressure must only against the power work of the return spring 29, because existing in the regulation chamber 33 And storage tank pressure at the compression fittings P of the hydraulic press 10 is fitted over by branch.The thus regulation is especially rapidly carried out.
Only when the hydraulic press 10 has reached negative swept volume and thus ensure that：The hydraulic press is not in motor Can be applied torsion moment on the internal combustion engine 4 against normal rotation direction in operation, especially when the hydraulic press is in When in maximum negative swept volume, the memory stop valve 22 enters in such position：Wherein, from hydraulic storage 16 Pressure medium flow towards the compression fittings P of the hydraulic press 10 is feasible.If the hydraulic press matches somebody with somebody position sensor （The swept volume is detected using the position sensor）, then the memory stop valve 22 be able to rely on the position sensor Signal connect.In addition, its certain period ground is connected at the rear of the control valve 48, ensures to reach by this period Negative swept volume, especially maximum negative swept volume.By the consumable component stop valve 20 in its rest position, it is ensured that It is that will not inadvertently cause the motion of one of consumable component 1 and 2 of the hydraulic pressure.
After the memory stop valve 44 is opened, the hydraulic press 10 starts to drive the internal combustion as hydraulic motor Machine.Connecting the memory stop valve 44 in the near future, the pressure limit valve 62 is so manipulated by the controller 50：Make Obtain pressure（It is set on the pressure）With fixed pressure differential（In currently such as 35 bar）Passed positioned at by the pressure Below memory pressure detected by sensor 75.1.6 times so big of the pressure differential thus about described pump Δ p.Cause Declined by the pressure medium of the hydraulic press by taking out flowing for the memory pressure, thus be set at the pressure Pressure at power restriction valve 62 is also continuously reduced.Here to point out, due to by the He of memory stop valve 22 The pressure drop that the nozzle that may be structured between the memory stop valve and the hydraulic storage is carried out, in the storage The pressure in track section between device stop valve 22 and the hydraulic press 10 is less than the memory pressure, and the pressure Drop with the internal combustion engine and thus the increase of the rotating speed of the hydraulic press and increase because flowing by the memory cut-off The pressure medium amount increase of valve.Pressure differential between memory pressure and the pressure being set at the pressure limit valve this When be chosen such that：So that the pressure that the compression fittings P of the hydraulic press 10 is fitted over by branch is applied in the LS regulating valves Power, less than the power applied by the LS control pressures and the summation of the power of the regulation spring 41.The LS regulating valves 40 Therefore in position shown in the figure：In the position, the joint 46 is towards storage tank off-load.
As long as internal combustion engine reaches startup rotating speed, 400 revolutions for example per minute（The internal combustion engine from the startup rotating speed Accelerating running is until idler revolutions in the case of not having other drive device）, then it is described to control valve 48 to be again introduced into its basis In position and thus the regulation chamber 30 separated with the hydraulic storage 16 and with the pressure-feed throttle regulator 45 Joint 46 be connected.Equally, from this moment, pressure value（The pressure limit valve 62 is set in the pressure value just）No It is further continued for changing.Because the hydraulic press 10 keeps in negative swept volume first, then the pressure at the high pressure connection P Continue to be less than the memory pressure.Additionally, the memory pressure declines and then the pump pressure also continues to decline. This, if the LS control pressures drop to below now set at the pressure limit valve 62 and constant value of holding （Because the pressure of the pressure less than the setting at the pressure limit valve 62 of the input end in the LS valves 44）, then this holding Without the influence of the position to the LS regulating valves 40, because while now described two pressure being present at this valve may About formed objects, but the position of the valve is maintained in the presence of the regulation spring 41.
After the control valve 48 enters in its base position, thus the regulation chamber 30 is by the control He of valve 48 The LS regulating valves 40 can immediately begin to towards the storage tank off-load, and the back swing process of the hydraulic press.Institute State in the regulation chamber 33 at regulating piston 28, there is the pressure for propping up and fitting at the compression fittings P.This pressure is together with return bullet Spring 29 works towards the direction that the stroke control element is adjusted towards the direction of zero swept volume.Because generally acting as Restoring force is very big, then the acceleration of the stroke control element is larger, so as to the reset of big dynamic implement.
Spacing in time after the control valve 48 is returned in its base position（Institute is ensured by the spacing Hydraulic press 10 is stated to be adjusted towards positive swept volume）In, the memory stop valve 22 is again introduced into its base position.Thus protect Card, until during the whole reseting stage of zero swept volume, pressure is there is in the pressure line 14.Thus, Avoid the hole at the hydraulic press.Additionally, as described above, being acted at the stroke control element has Larger power.
When the hydraulic press 10 back swings, from the hydraulic storage 16 towards the pressure medium flow of the hydraulic press It is continuously reduced, and zero is equal in zero swept volume.Corresponding to this, between the pump pressure of memory pressure and hydraulic press 10 Pressure differential it is less and less and in zero swept volume be equal to zero.Until reaching startup rotating speed during starting process, depositing The constant pressure differential that keeps between reservoir pressure and the pressure being set at the pressure limit valve is now chosen such that： So that after the control valve 48 is back switched in base position, being now constantly maintained at the pressure limit valve Pressure value about with the pump Δ p be located at the memory pressure below, reach zero when the hydraulic press is in the reset During swept volume.It hereby is obtained that, the hydraulic press 10 is not actuated in the positive swept volume of maximum, and is held in institute State below such as percent 45 positive swept volume of the positive swept volume of maximum, the positive swept volume can cause the diesel oil horse Up to static again.If when zero swept volume is reached, pump pressure and by set the pressure limit valve 62 and quilt Difference between previously given LS control pressures is slightly less than the pump Δ p, then the hydraulic press 10 as pump it is less just Feed some amount during swept volume, the pump Δ p is corresponded to be set up between the pump pressure and the LS control pressures Difference.If in pump pressure and previously given by setting the pressure limit valve 62 when close to zero swept volume Difference between LS control pressures is slightly less than the pump Δ p, then the hydraulic press 10 as motor in less negative swept volume When also swallow some amount, so as between the pump pressure and the LS control pressures set up corresponding to the pump Δ p difference.
Such state is reached in any situation：Wherein, the hydraulic press 10 is lucky in small positive swept volume The so many pressure medium amount of feed：So that balance inside leakage and be maintained pump pressure, the pump pressure is with the pump Δ p Positioned at by set the pressure limit valve 62 and it is more than previously given value.Next, the setting of the pressure limit valve 62 By being ramped down in almost zero pressure value, and correspondingly, the pump pressure is also reduced to relatively low standby pressure On.Accordingly, the consumable component stop valve 20 is entered into its feed-through locations.
The drive device of hydrostatic of the invention is especially also suitable for use with first in specific structural scheme In the vehicle used in bus, rail vehicle or by delivery service business, namely in such vehicle：Usually utilizing should Vehicle is stopped and is leaveed again.
Reference list
1 hydraulic control device
2 other consumable component
4 diesel motors
6 bent axles
8 power transmission shafts
10 hydraulic presses
12 shells
13 storage tanks
14 pressure lines
16 high pressure accumulators
18 branches
20 consumable component stop valves
22 memory stop valves
26 first regulating pistons
28 second regulating pistons
29 return springs
30 regulation chambers
31 valve gears
32 chamber joints
33 regulation chambers
36 LS reporting lines
38 reversal valves
39 pressure-regulating valves
40 LS regulating valves
44 LS valves
45 pressure-feed throttle regulator
46 45 joint
48 control valves
52 start stopping valve block
54 reversal valves
56 LS reporting lines
62 pressure limit valves
64 nozzles
66 48 joint
67 circuits
75 pressure sensors
76 temperature sensors
80 control units
The circuit of 81 electricity
The circuit of 82 electricity
The circuit of 83 electricity
T storage tank joints
P compression fittings
X LS joints

Claims (11)

1. a kind of drive device of hydrostatic, the drive device is particularly for starting internal combustion engine（4）, the drive device has liquid Press（10）, the hydraulic press by means of hydraulic pressure adjusting means in the swept volume of the hydraulic press from maximum positive swept volume The negative swept volume of maximum can be adjusted by zero swept volume, the hydraulic press can be used as pump operation by the use of positive swept volume And can be used as motor operation by the use of negative swept volume, the drive device has at least one high pressure accumulator（16）, it is right In the operation as hydraulic motor, pass through in the hydraulic press from the high pressure accumulator（10）Compression fittings（P）With the height Pressure memory（16）Between move towards pressure line（14）The hydraulic press can be supplied using pressure medium（10）, the driving Device has the memory stop valve with first position and the second place（22）, the memory stop valve is arranged in the pressure Circuit（14）In and caused from the high pressure accumulator by the memory stop valve（16）Towards hydraulic press（10）Fluid Connecting portion is opened in the first position and ended in the second place, and the drive device has electronics Control unit（80）, depending on the signal of the control unit can operate the memory stop valve（22）, it is characterised in that By hydraulic press（10）When being adjusted from negative swept volume towards positive swept volume, the controller of the electronics（80）Now providing is used for By the memory stop valve（22）The signal in the second place is switched to from first position so that the memory stop valve （22）In the hydraulic press（10）Zero swept volume or positive swept volume in the case of be just switched to the second place In.
2. according to the drive device of the hydrostatic described in claim 1, wherein, the adjusting means includes that being abutted to regulation lives Plug（26）First regulation chamber（30）, be abutted to regulating piston（28）Second regulation chamber（33）And return spring（29）, this time Position spring works towards the direction of maximum positive swept volume, for the described first regulation chamber, by valve gear（31） Can control to facilitate the pressure medium being adjusted towards the direction of maximum negative swept volume influent stream and being capable of the row of control Stream, it is described second regulation chamber constantly with the compression fittings（P）Fluidly connect and the second regulation chamber is towards maximum Reduce in the regulation in the direction of negative swept volume and increase in the regulation towards the direction of maximum positive swept volume.
3. according to the drive device of the hydrostatic described in claim 2, wherein, the valve gear（31）Including control valve （48）, by the control valve, do not rely on compression fittings（P）, from pressure medium source（16）In can using pressure medium for The hydraulic press（10）Supplied, for adjusting chamber towards first（30）Negative swept volume regulation.
4. according to the drive device of the hydrostatic described in claim 3, wherein, the valve gear（31）For the hydraulic press （10）Include with joint as the operation of pump（46）Hydraulic pressure adjuster（45）, wherein, the control valve（48）It is No. 3/2 valve, the control valve carries the first joint, the adjuster of first joint and the hydraulic pressure（45）Joint（46）Fluid connects Connect, and the control valve carries the second joint（66）, second joint and the pressure medium source（16）Fluidly connect, and should Control valve carries the 3rd joint, the 3rd joint and the described first regulation chamber（30）It is connected, and wherein, the control valve（48） With first position, in the first position, the 3rd joint and the first joint are fluidly connected and the second joint（66）Quilt Cut-off, and the control valve has the second place, in the second place, the 3rd joint and the second joint（66）It is connected And first joint is cut off.
5. according to the drive device of the hydrostatic described in claim 4, wherein, the adjuster of the hydraulic pressure（45）Including load Sensing（LS）Regulating valve（40）, the load-sensing（LS）Regulating valve flows to the first regulation chamber of the adjusting means in pressure medium （30）Meaning in by the compression fittings（P）The pressure-loaded at place, and in pressure medium from the described first regulation chamber （30）By regulation spring in the meaning of middle outflow（41）Be present in LS joints（X）The LS control pressures loading at place, and wherein, In the hydraulic press（10）Negative swept volume in the case of also LS control pressures are given to the load-sensing（LS）Regulation Valve（40）LS joints（X）.
6. according to the drive device of the hydrostatic described in claim 5, wherein, in the control valve（48）It is also located at the control When in the second place of valve, the load-sensing is loaded using LS control pressures（LS）Regulating valve（40）.
7. according to the drive device of the hydrostatic described in claim 5 or 6, wherein, when the hydraulic press（10）In past backswing When reaching zero swept volume from maximum negative swept volume when dynamic, it is given to the LS joints（X）The LS control pressures About adjusting spring（41）Pressure equivalent and be less than in the compression fittings（P）The pressure at place, so that the hydraulic press （10）Be conditioned by zero swept volume, but simultaneously non-regulated until maximum positive swept volume.
8. according to the drive device of the hydrostatic described in claim 5 or 6, wherein, when the control valve（48）It is also located at this When in the second place of control valve, LS control pressures have been given to the load-sensing（LS）Regulating valve（40）LS joints （X）, wherein, the LS control pressures first with fixed pressure differential, in the high pressure accumulator（16）In pressure below, with With the memory pressure for declining, and wherein, when the control valve（48）Changed to the control from the second place of the control valve When in the first position of valve, the LS control pressures keep constant.
9. according to the drive device of the hydrostatic described in claim 8, wherein, the pressure differential of the fixation is about described bearing Carry sensing（LS）The regulation spring of regulating valve（41）1.6 times so big of pressure equivalent.
10. according to the drive device of hydrostatic in any one of the preceding claims wherein, wherein, the hydraulic press is with useful In the logger of swept volume, and wherein, after control valve is switched in first position from the second place, the LS controls The change of the size or negative swept volume that are sized depending on negative swept volume of pressing pressure determines.
11. according to hydrostatic in any one of the preceding claims wherein drive device, wherein, the hydraulic press is with useful In the logger of swept volume, and wherein, after control valve is switched in first position from the second place, the storage Device stop valve depends on the size of detected swept volume to be switched in the second place from first position.
CN201580049475.2A 2014-09-15 2015-08-04 The driving device of hydrostatic Active CN106715925B (en)

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DE102014218419.3A DE102014218419A1 (en) 2014-09-15 2014-09-15 Hydrostatic drive
PCT/EP2015/067919 WO2016041685A1 (en) 2014-09-15 2015-08-04 Hydrostatic drive

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CN106715925B (en) 2018-08-17
US10161372B2 (en) 2018-12-25
US20170254308A1 (en) 2017-09-07
WO2016041685A1 (en) 2016-03-24
EP3194758B1 (en) 2018-10-24
DE102014218419A1 (en) 2016-03-17

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